CN202579183U - Compressor - Google Patents

Abstract

The utility model relates to a compressor. An external heat exchanger is used for transferring heat from a lubricating agent of the compressor to an expansion working fluid, so as to cool the lubricating agent. The heat exchanger is also used for secondarily cooling the condensed working fluid by utilizing the same expansion working fluid. A horizontal scroll compressor comprises a middle lubricating agent slot between a main bearing base and a vortex component. A counterweight on a crank shaft can pass through the lubricating agent in the middle lubricating agent slot so as to splash the lubricating agent to the surrounding. The horizontal scroll compressor can comprise a plurality of processing surfaces for accurately centering and aligning the parts of the compressor.

Description

Compressor

The application is that the application number of submitting on May 17th, 2010 is 201020208698.3, is entitled as the dividing an application of one Chinese patent application of " compressor and oil cooling system ".

Technical field

The utility model relates generally to compressor.

Background technique

Usually, compressor, particularly scroll compressor are usually placed in the shell of sealing or semitight, and this shell defines the chamber of ccontaining working fluid.Dividing plate in the said shell is divided into discharge pressure district and suction pressure district with said chamber usually.In downside was arranged, scroll component was positioned at said suction pressure district and is used for compression working fluid.Generally speaking; These scroll components are combined with a pair of intermeshing spiral scrollwork; In the said a pair of scrollwork one or two with respect to another around moving; Thereby limit one or more mobile cavities, the size of said mobile cavity reduces when the center discharge port moves from outside inhalation port at them gradually.Usually provide electric notor to operate and facilitate this phase opposing connection moving.

The compressed fluid that dividing plate in the said shell allows to leave the center discharge port of said scroll component gets into the discharge pressure district in the shell, keeps the integrity between said discharge pressure district and the said suction pressure district simultaneously.This of said dividing plate function is usually by realizing with dividing plate and the interactional Sealing of scroll element that limits said center discharge port.

The discharge pressure district of said shell is typically provided with the exhaust fluid port, and this exhaust fluid port is communicated with the fluid circuit of refrigerating circuit or certain other types.In locking system; The end opposite utilization of said fluid circuit is passed the suction fluid port that shell extends to the suction pressure district of shell and is linked to each other with the suction pressure district of shell; Therefore; Said scroll compressor receives the working fluid from the suction pressure district of shell, and compression working fluid in the said one or more mobile cavities that limited scroll component is discharged into the working fluid that compresses the discharge pressure district of compressor then.The working fluid of compression is directed passing said discharge port through said fluid circuit, and turns back to the suction pressure district of shell via said inhalation port.

Can make with lubricator (for example oil) groove come the charging of stored oiling agent at the shell of said compressor.Said groove can be placed on said low pressure zone or said high pressure district.Said oiling agent is used for the moving element of lubricated said compressor, and flows through said scroll component and be discharged into the discharge pressure district of said compressor with said working fluid.The temperature of the oiling agent of discharging is raised with the temperature of said working fluid.Before said oiling agent refluxes through said compressor and lubricated wherein parts, oiling agent cooled off to reduce and suck the overheated of gas, thereby improve compressor volume efficient and more performance is provided.Through cooling off said suction gas and motor, the reduction of said lubricant temperature can also improve the reliability of compressor.Cool off the viscosity that said oiling agent can also keep oiling agent and be in the desirable level of keeping oil slick thickness between the moving member.

In said compressor, oiling agent offers various moving elements.Improve performance and/or its life-span of the oiling agent distribution in whole compressor advantageously raising compressor.

In said compressor, various parts correct aligning relative to each other can improve the performance of compressor and/or reduce the sound by compressor produced.Improving various parts for example decides aligning between scroll element, bearing and the motor and can improve the performance of compressor and/or reduce the sound by compressor produced.Said compressor usually uses a large amount of discrete parts, thereby these parts fit together in the enclosure aligning is provided.Yet; Use these a large amount of independent and discrete parts to increase the coarse possibility of component alignment; And further, owing to need tolerance stricter between the various parts producing desired aligning, its manufacturing maybe be more expensive or be expended more time.

The model utility content

In one form, the utility model provides a kind of system that comprises compressor, oiling agent, condenser, expansion gear and heat exchanger.Said compressor can be compressed to the discharge pressure that is higher than said suction pressure with working fluid from suction pressure.Said oiling agent can lubricate said compressor.The condensable working fluid of said condenser by said compressor discharge.The inflatable expanded working fluid of said expansion gear by said condenser condenses.Said heat exchanger can be delivered to expanded working fluid from said oiling agent with heat.

In another form, the disclosure provides a kind of compressor that comprises shell, compressing mechanism, bent axle, bearing and lubricant tank.Said compressing mechanism can be arranged in the said shell and compression working fluid.Said bent axle can be arranged at least in part in the said shell and with said compressing mechanism driven nature engage.Said bearing support rotatably supports said bent axle.Said lubricant tank can keep the oiling agent of certain volume and be arranged in said bearing support and said compressing mechanism between.

In another form, the disclosure provides a kind of compressor that comprises the integral type main body, and this main body can comprise the shell integrally formed with main bearing seat.Said main bearing seat can comprise the hole of a part that is used to support bent axle.Said shell can comprise the continuous circular shape surface of the first end of contiguous said shell on the inside of said shell and a plurality of axially extended arcuate surface of the second end of contiguous said shell.Said a plurality of arcuate surface is opened along the said internal layout of said shell.

Said compressor also can comprise the scroll element with outer surface, and the size of said outer surface is set to be coupled in the said first end of said shell and with said annular surface and engages.Said annular surface can make said scroll element centering in said shell.

Said compressor also can comprise the dividing plate with edge, and the size at said edge is set to be coupled in the said first end of said shell and with said annular surface and engages.Said annular surface can make said dividing plate with respect to said shell centering.

Said compressor also can comprise the end cap with edge, and the size at said edge is set to be coupled in the said the second end of said shell and with said arcuate surface and engages.Said end cap can have the hole of the end that is used to support said bent axle.Said arcuate surface can make said end cap with respect to said shell centering and said hole and the said hole in the said main bearing seat in the said end cap are axially aligned.

Said compressor also can comprise the stator with outer surface, and the size of said outer surface is set to be contained in the said shell.Said outer surface can engage with said arcuate surface.Said arcuate surface can make said stator centering in said shell.

Said compressor further comprises: the shoulder in the said shell between said main bearing seat and said annular surface; And thrust plate, said thrust plate has first surface that engages with said scroll element and the second surface that engages with said shoulder, and said shoulder limits the axial position of said thrust plate in said shell.

Preferably, said main bearing seat and said thrust plate limit the downside lubricant tank jointly.

Said compressor further comprises bent axle and counterweight; Said bent axle engages with said scroll element driven nature; Said counterweight attaches to said bent axle and rotates along with the rotation of said bent axle; Said counterweight is passed the oiling agent in the said downside lubricant tank and wherein the said oiling agent of splashing during said crankshaft rotating, thus with said lubricant delivery to said scroll element.

Preferably, said end cap is limited with high side lubricant tank.

Preferably, said end cap comprises the oiling agent outlet fitting that is communicated with said high side lubricant tank and heat exchanger fluid.

Preferably, said heat exchanger comprises the first fluid passage and second fluid passage that receive from the working fluid of said compressor of reception from the oiling agent of said high side lubricant tank, and the said first fluid passage and second fluid passage be fluid isolation each other.

Preferably, said scroll element is limited with the intermediate pressure position of reception from the expanded working fluid of said heat exchanger.

But the utility model further application will become clearly from the detailed description that hereinafter provides.Yet should be understood that; Although description that these are detailed and concrete example have been pointed out the preferred implementation of the utility model; But only just for purposes of illustration; Because through the detailed description here, the variations and modifications in the utility model purport and the scope will become obvious to those skilled in the art.

Description of drawings

Figure described here just is used for purpose that selected mode of execution rather than all possible mode are described, and is not intended to restriction the scope of the present disclosure.

Figure 1A-1C is the external structure according to the compressor of the utility model;

Fig. 2 is the sectional view along the line 2-2 of Fig. 1 C;

Fig. 3 A and Fig. 3 B are the external structures of the shell of compressor shown in Figure 1A-1C;

Fig. 3 C is the end elevation of housing shown in Fig. 3 A;

Fig. 4 is the end elevation of the another kind of mode of execution of housing shown in Fig. 3 C;

Fig. 5 is the external structure of the low side cover of compressor shown in Figure 1A-1C;

Fig. 6 is the external structure of the dividing plate of compressor shown in Figure 1A-1C;

Fig. 7 and Fig. 8 are the external structures of deciding vortex of compressor shown in Figure 1A-1C;

Fig. 9 is the sectional view along the line 9-9 of Fig. 8;

Figure 10 is the partial section of amplification of the part of compressor shown in Figure 1A-1C, has shown the characteristic of deciding vortex and dividing plate;

Figure 11 is the sectional view along the line 11-11 of Fig. 3 A;

Figure 12 is the external structure of the thrust plate of compressor shown in Figure 1A-1C;

Figure 13 is the external structure of another kind of mode of execution of the thrust plate of compressor;

Figure 14 is the schematic representation according to cooling system in the refrigeration system of the utility model, that be used for using with the compressor shown in Figure 1A-1C; And

Figure 15 be according in the refrigeration system of the utility model, be used for using schematic representation at another cooling system of the oiling agent of the compressor shown in Figure 1A-1C.

Embodiment

Below describe and be in fact exemplary and never be intended to limit the disclosure, its application or use.

With reference to figure 1A-1C, Fig. 2-3 and Figure 10, it has shown thecompressor 20 according to theutility model.Compressor 20 is a kind of semi-closed compressors with housing orshell 22, andshell 22 hasopposite end 23,25, and downside (LS)end cap 24 attaches toend 23, andpartition component 26 attaches to end 25 with high side (HS) end cap 28.LSend cap 24, dividingplate 26 andHS end cap 28 can attach toshell 22 through the fastening piece of bolt or other type well known in the art.Other primary component that is fixed inshell 22 comprises Working-fluid intakingaccessory 30,heat exchanger 32 and theelectronic box 31 that can be positioned at the inner or outside members ofcompressor 20 with sensor andother.LS end cap 24 compriseslubricant entry accessory 34, andHS end cap 28 can be limited with high side lubricant tank and comprise lubricant outlet accessory 36.HS end cap 28 also can comprise working fluid outlet fitting 38 and sight gauge 40.Dividing plate 26 can comprise fluidinjection inlet accessory 42, and is as described below, and the intermediate pressure position in the compression element ofaccessory 42 and compressor is communicated with.HS end cap 28limits drain chamber 46 with dividingplate 26, andLS end cap 24,shell 22 and dividingplate 26 limit suction orsuction chamber 48.

With reference to figure 2-4 and Figure 11,shell 22 is single one-piece element or single-pieces, has various machining feature therein, and as nonrestrictive example,shell 22 can be a cast component.Thereby the inner member that various characteristics can be processed inshell 22 to being assemblied in the shell provides accurate aligning.Shell 22 comprisesmain bearing seat 50, has precision machinedcentral opening 52 therein, and opening 52 is configured to hold main bearing oraxle sleeve 54, and to support the intermediate portion ofbent axle 56, bearing 54 can be press fitted in theopening 52.

Main bearing seat 50 also can comprise a plurality oftop edge openings 58, and it is convenient to working fluid and lubricantflow time shell 22 and compressor 20.Be described below, thebottom 59 of main bearing 50 is solid in case fluid flows through, and limits the part of central oiling agent groove.Although Fig. 3 C has described to comprise themain bearing seat 50 of threeopenings 58,main bearing seat 50 also can as shown in Figure 4ly comprise four openings 58.Fouropenings 58 shown in Figure 4 can be set to the style of vertical simultaneously symmetry and horizontal symmetrical (with respect to view shown in Figure 4).The layout ofsuch opening 58 has kept wholemain bearing seat 50 to have consistent relatively hardness, thereby the equally distributed support to bearing 54 andbent axle 56 is provided.In unshowned in the drawings other mode of execution,main bearing seat 50 can comprise theopening 58 of other quantity and layout.Thehole 58 that for example, threeholes 58 or any other quantity can be set is come withbent axle 56 consistent relatively support to be provided for bearing 54.

Shell 22 also comprises the precision machinedsurface 60 of adjacent end 25.Surface 60 is cylindrical and is used as the guided rings of compressor 20.Whatsurface 60 provided that precision surface is used to installscroll component 64 decides vortex or non-moving vortex 62.Surface 60 also provides precision surface to be used to install dividing plate 26.Precision machining is takeed on 65 neighbouringsurfaces 60 and is provided precision surface to be used atshell 22thrust plate 112 being installed.Shell 22 also comprises the precision machinedsurface 66 of a plurality of contiguous first ends 23.Accurate aligning and the centering ofstator 68 inshell 22 that eachsurface 66 forms a cylindrical part and provides precision surface to be used formotor 70 jointly.Surface 66 also provides precision surface to be used for the accurate aligning and the centering of LS end cap 24.End 23,25 also is a finished surface, is used for the attached ofLS end cap 24 and dividingplate 26 andHS end cap 28 andshell 22.

With reference now to Fig. 2 and Fig. 5,,LS end cap 24 comprisescenter shrinkage pool 72 and outwardsoutstanding ring edge 74, and the border ofring edge 74 limitingholes 72 also separates withperiphery 76 radial inward of LS end cap 24.Engaging surface 78 extends between 74 and peripheral 76 on the edge of.Engaging surface 78 is configured to engage with theend 23 of shell 22.As nonrestrictive example, packing ring or other seal arrangement can be arranged betweensurface 78 and theend 23 so that the tight of the liquid between them to be provided.Hole 72 is the precision machined surface in theLS end cap 24 withedge 74 andLS end cap 24 and the accurate centering ofbent axle 56 incompressor 20 is provided.Especially, bearing oraxle sleeve 82 are press-fit in thehole 72 and theend 96 ofbent axle 56 is arranged in the bearing 82.Edge 73 engages a plurality of surperficial 66 thereby the accurate centering of LS end cap with respect toshell 22 is provided, and makes thathole 72 is aimed atcentral opening 52 andbent axle 56 accurately is positioned in thecompressor 20.

Motor 70 comprisesstator 68 and is press-fit to the rotor 84 on the bent axle 56.Stator 68 is press-fit in theshell 22, and the outer surface ofstator 68 engages with a plurality of surperficial 66 simultaneously.Like this,surface 66 can provide the accurate centering ofstator 68 in shell 22.The precision machined surface at opening 52,surface 66,hole 72 andedge 74 helps bentaxle 56 and themotor 70 accurate aligning incompressor 20; Make when aiming at, have accurate gap between rotor 84 and thestator 68 with other parts ofcompressor 20 are suitable.

With reference to figure 2,bent axle 56 has eccentric crank pin 86 at one end thereof 88 places.Describe in detail more as following; Crank pin 86 rotatably is coupling (journaled) in the internal holes that is generally D shape ofpropeller shaft sleeve 90;Propeller shaft sleeve 90 is arranged in the driving bearing 91, and driving bearing 91 is pressed in themoving vortex 92 that is engaged in scroll component 64.Propeller shaft sleeve 90 has circular outer diameter.The intermediate portion 94 ofbent axle 56 rotatably is coupling in thebearing 54 of the opening 52 of main bearing seat 50.Theother end 96 ofbent axle 56 rotatably is coupling in thebearing 82 in thehole 72 ofLS end cap 24.

Bentaxle 56 hasconcentric holes 98 at relatively large 96 places, end of its diameter, and it is communicated with the radially outer smaller diameter bore 100 that extends to end 88.The internal lubricant passage 102 that hole 98,100 forms in the bent axle 56.Oiling agent is fed tohole 98 through thelubricant passageway 104 that is communicated withinlet fitting 34 in theLS end cap 24.

Bentaxle 56 is rotatably driven by theelectric notor 70 that comprises rotor 84 and stator 68.First counterweight 106 is coupled to rotor 84, thesecond counterweights 108 at 96 places, end ofcontiguous bent axle 56 and between end 88 and intermediate portion 94, attaches tobent axle 56.

With reference now to Fig. 2 and Figure 11-12,,thrust plate 112 is arranged in thecompressor 20 against theprocessing shoulder 65 betweenend 25 and the main bearing seat 50.As unrestriced example, the fastening piece thatthrust plate 112 can engage through thehole 116 of the complementation in a plurality of and theshell 22 is fastened in the shell 22.Thereforethrust plate 112 can be fixedly secured inshell 22, and the surface ofthrust plate 112 is againstshoulder 65 simultaneously.The opposition side ofthrust plate 112 comprises the annularthrust supporting surface 114 of the movingvortex 92 of axiallysupport.Thrust plate 112 comprisescentral opening 120 and a plurality of top edge openings 122.Opening 122 is arranged on thethrust plate 112, makesthrust plate 112 have to be positioned at the followingsolid part 124 ofcentral opening 120 belows.Be described below,solid part 124 defines the part of central oilingagent groove.Opening 122 allows fluids, and for example oiling agent and working fluid flow throughwhole compressor 20.

Though what Figure 12 described is thethrust plate 112 that comprises threeopenings 122,thrust plate 112 shown in Figure 13 has four openings 122.Fouropenings 122 shown in Figure 13 can be set to the mode thatwhole thrust plate 112 provides relatively consistent hardness, thereby equally distributed relatively support are provided and reduce to be applied to by movingvortex 92 the inhomogeneous deflection of thethrust plate 112 that the axial force on the thrust plate causes for moving vortex 92.In unshowned in the drawings other mode of execution,thrust plate 112 can comprise the opening 122 of other number and layout.For example, three holes 112 (orhole 112 of any other number) can be set thus relatively consistent hardness is provided and equally distributed support is provided for movingvortex 92 forwhole thrust plate 112.

Movingvortex 92 is included in firstspiral wraps 128 on its first surface.The apparent surface of movingvortex 92 or second surface engage with thethrust supporting surface 114 ofthrust plate 112 and comprise and stretch out from here and extend to the cylindrical hub 130 in thecentral opening 120 of thrust plate 112.Axle sleeve 90 rotatably is arranged in the cylindrical hub 130, is arranged in theaxle sleeve 90 to bent axle 86 driven natures.Crankpin 86 has the par on a surface, its with the plat surface driven nature of internal holes engage, so that the drive arrangement of radial compliance to be provided; For example at assignee's United States Patent(USP) No. 4; Shown in 877,382, this patent is incorporated in this mode through reference.

Oldhamcoupling 136 is arranged between movingvortex 92 and the thrust plate 112.Oldhamcoupling 136 utilizes key to be connected in movingvortex 92 and decidesvortex 62, in case the rotatablely moving of fastening vortex 62.Oldhamcoupling 136 is disclosed type in assignee's the United States Patent(USP) No. 5,320,506 preferably, and this patent is incorporated in this mode throughreference.Black box 138 is used for sealingground suction chamber 48 anddrain chamber 46 is separated by deciding theseat portion 140 thatvortex 62 supported and engaged dividing plate 26.Black box 138 can with assignee's U.S. Patent application No.12/207, disclosed black box is identical in 051, this patent application is incorporated in this mode through reference.

With reference now to Fig. 2 and Fig. 7-10,, to decidevortex 62 and comprise secondspiral wraps 142, it is positioned to and moves first spiral wraps, 128 engagements of vortex 92.Decide discharge passage or port one 44 thatvortex 62 has the centered that is limited substrate portion 146.Decidevortex 62 and also comprise ring-shaped hub 148 around discharge passage 144.Integrated type shutoff device orescape cock 150 can be set in discharge passage 144.Escape cock 150 is depicted as normally close valve.During compressor operating, depend on pressure difference and the design ofescape cock 150 betweendischarge passage 144 and thedrain chamber 46, said valve can be shown in an open position or closed position.Whencompressor 20 quit work,escape cock 150 cut out.

Decide the periphery surface 154 thatvortex 62 comprises processing, it is designed and sized tosurface 60 Spielpassung with shell 22.Becausevortex 62 accurate centering incompressor 20 is decided in the fine finishing ofsurface 60 and periphery surface 154.Decide theopening 156 thatvortex 62 comprises adjacent perimeter surface 154 and extends through substrate portion 146.Opening 156 is configured to holdanti-rotating dog 157, andanti-rotating dog 157 extends from dividingplate 26, is used foranti-fastening vortex 62 and incompressor 20, rotates.Discharge aperture 158 extend throughsubstrate portion 146 and allowfirst scrollwork 128 andsecond scrollwork 142 between compressed fluid be discharged in theintermediate cavity 160 of deciding betweenvortex 62 and the dividing plate 26.Leak 158 allows pressure fluid to get intochamber 160 and decidesvortex 62 towards movingvortex 92 bias voltages.

Decide vortex 62 and comprise that first radially extendspassage 162,passage 162 can hold measures near thetemperature probe 164 of decidingvortex 62 temperature in discharge pressure district.As nonrestrictive example,temperature probe 164 can be positive temperature coefficient thermistor, negative temperature coefficient thermistor or thermocouple.Decidevortex 62 and can comprise secondradial passage 166 that is communicated with two branches 168,170.Passage 166 is communicated with the inlet fitting that extends through dividingplate 26 42.The end of each in branch 168,170 has a pair of opening 172 that extends axially, and opening 172 extends in the compression chamber that is formed betweenfirst scrollwork 128 and second scrollwork 142.Passage 166,branch 168,branch 170 and and opening 172 allow fluids to be expelled to the compression chamber that is arranged in intermediate pressure position betweenfirst scrollwork 128 andsecond scrollwork 142.

With reference now to Fig. 2, Fig. 6 and Figure 10,, dividingplate 26 is included near processingengaging surface 176 that extends the periphery and the ring edge that is processed intoprotuberance 178 that extends from engaging surface 176.Engaging surface 176 engages with theend 25 of shell 22.As nonrestrictive example, packing ring or other seal arrangement can betweensurface 176 andend 25, be arranged, so that the tight of the liquid between them to be provided.Edge 178 engages with the precision machinedsurface 60 ofshell 22, so that the accurate centering of dividingplate 26 with respect toshell 22 to be provided.The size atedge 178 is set to form Spielpassung with thesurface 60 of shell 22.Edge 178 can with decide on thevortex 62 contiguous its peripheralengaging surface 192 axial engagement.Edge 178 has limited with engaging ofengaging surface 192 decides the axially locating ofvortex 62 in shell 22.Dividingplate 26 comprisescenter base portion 140, andcenter base portion 140 allows pressure fluid to decide the part of theintermediate cavity 160 ofvortex 62 towards movingvortex 92 bias voltages in the face of decidingvortex 62 and forming.Dividingplate 26 comprises near a plurality ofopenings 182 of periphery that are positioned at, and is used for utilizing fastening piece to be fastened toshell 22 with HS end cap 28.Dividing plate 26 comprises theopening 184 that is arranged inedge 178, and opening 184 is configured to holdanti-rotating dog 157, andanti-rotating dog 157 engages with decidingvortex 62interior openings 156, in case fasteningvortex 62 rotates in compressor 20.A pair of radial passage 186,188 is arranged on the periphery of dividingplate 26, is used for holding respectivelytemperature probe 164 and theinlet fitting 42 that is coupled to internal flow injection tube 187.Dividingplate 26 comprises secondengaging surface 190 of the opposite side that is positioned at engaging surface 176.Engaging surface 190 processing also is configured to engage with the processingengaging surface 194 of the complementation of HS end cap 28.As nonrestrictive example, packing ring or other seal arrangement can be arranged inengaging surface 190, between 194, so that the tight of the liquid between them to be provided.

Dividing plate 26 comprisescentral opening 198, and opening 198 is communicated withdischarge passage 144 andescape cock 150 in the one of which side, is communicated with fluid filter/separator 200 in its opposite side.Dividingplate 26 was openedsuction chamber 48 and drain chamber in 46 minutes.

Atcompressor 20 duration of works; Thevortex import 202 undersuction chamber 48 processes of working fluid and oiling agent flows to the chamber that is formed betweenfirst scrollwork 128 andsecond scrollwork 142, and theopening 198 in thedischarge passage 144 of flowing through then,escape cock 150 dischargings and the dividingplate 26 also gets into theseparator 200 in the drain chamber 46.Inseparator 200, the bottom that oiling agent separates with working fluid and fallsdrain chamber 46 through gravity, and working fluid is discharged through the outlet fitting theHS end cap 28 38 fromdrain chamber 46.

With reference to figure 1A-1C and Fig. 2, theoutlet accessory 36 in theHS end cap 28 anddrain chamber 46 with and interior oiling agent be communicated with.Oiling agent circuit 210 extends to the top ofheat exchanger 32 throughaccessory 212 from outlet accessory 36.Oilingagent return line 214 extends to the inlet fitting 34 on theLS end cap 24 from theaccessory 216 onheat exchanger 32 bottoms.Drainchamber 46 is in discharge pressure andsuction chamber 48 is in suction pressure, and suction pressure is usually less than discharge pressure.Pressure difference makes oiling agent flow tosuction chamber 48 viaheat exchanger 32 from drain chamber 46.Especially, oiling agent flows through the path 10 4 in oilingagent circuit 210,heat exchanger 32,return line 214 and the LS end cap 24.Oiling agent flows into theend 96 of bearing 82 withlubricating bearings 82 andbent axle 56 from path 10 4.Oiling agent also flows in themacropore 98, when advance in the end 88 ofbent axle 56, flows throughaperture 100 at it then.When bentaxle 56 rotation, centrifugal force makes oiling agent flow toaperture 100 and flow on the end 88 from macropore 98.Oiling agent leaves end 88 and flows to aroundpropeller shaft sleeves 90 neutralizations in the hub 130 that movesvortex 92.

The oiling agent that flows out end 88 is fallen in the middle groove 222 through gravity.Middle groove 222 is limited thesolid part 124 ofthrust plate 112 and the solid lower portion of main bearing seat 50.Oiling agent can accumulate in the middle groove 222 atcompressor 20 duration of works.In the rotary course ofbent axle 56;Counterweight 108 is passed the oiling agent in the middle groove 222 and is splashed or rock its interior oiling agent and spreads all over the space between bearingsupport 50 and thethrust plate 112, makes that the interface between Oldham coupling 136 and thrustplate 112 and the movingvortex 92 receives oiling agent.Lubricant flow provides lubricated and cooling effect.

Oiling agent in thehole 72 ofLS end cap 24 can flow downward through gravity, and some oiling agents can accumulate in the bottom ofstator 68 and themotor zone 220 around the rotor84.Motor zone 220 is limited opposition side,shell 22 and theLS end cap 24 of the solidlower portion 59 of main bearing seat 50.Be described below, the oiling agent that leaveshole 72 is fallen the bottom ofshell 22 and is flow to the vortex side ofshell 22 viapassage 226.

Passage 226 extends between the far-end ofvortex import 202 under the vicinity ofmotor zone 220 and thrust plate 112.Passage 226 can pass themain bearing seat 50 ofshell 22 andprocess.Passage 226 is collected or is collected in the middle groove 222 with advantageously allowing some oiling agents separating of middle groove 222, is used for lubricating near middle groove 222 parts interior and or on every side via the rotation ofbent axle 56 and counterweight 108.The engaging of theshoulder 65 ofthrust plate 112 andshell 22 can provide half liquid to connect airtight and close; Wherein, When middle groove 222 in-lubricants compile; Still allow a part of oiling agent to flow out,, thereby continuous inflow is provided and flows out flowing of middle groove 222 because this part oiling agent is replaced by the new oiling agent that flows out from the end 88 of bent axle 56.Thereforesolid part 124 forms middle groove 222 withsolid part 59, and middle groove 222 can compile oiling agent therein atcompressor 20 duration of works.These characteristics can be cast inthrust plate 112 and the shell 22.As shown in Figure 2, the level of the nominal operation oiling agent level of middle groove 222 in the motor zone 220.Show the nominal operation oiling agent level in thedrain chamber 46 equally.

At work, thereby motor 70 is energized and causesbent axle 56 to begin around the rotation of its axis, therefore causes movingvortex 92 and 62 moves with respect to decide vortex.This rotation pulling working fluid gets into suction chamber48.In suction chamber 48, working fluid and mix lubricant are together and be pulled to down in thevortex import 202 and movingvortex 92 and deciding betweenfirst scrollwork 128 andsecond scrollwork 142 of vortex 62.Working fluid and oiling agent are compressed therein and are discharged into discharge pressure viadischarge passage 144 and escape cock 150.In working fluid and the oiling agentinflow lubricant separator 220 of discharging, wherein, working fluid passeslubricant separator 220 and oiling agent is trapped in wherein, and flows to the bottom ofdrain chamber 46 through gravity.Working fluid flows outdrain chamber 46 and gets into the system that usescompressor 20 through outlet fitting 38.If this system is the system of sealing, then working fluid is at thesuction chamber 48 that turns back tocompressor 20 through this system after by inlet fitting 30.

With reference now to Figure 1A-1C and Figure 14,, it has shown the cooling of oiling agent whencompressor 20 uses with exemplary refrigeration system 250.Refrigeration system 250 comprisescompressor 20, and the working fluid (like refrigeration agent) thatcompressor 20 will flow through wherein is compressed to the discharge pressure greater than suction pressure from suction pressure.Inlet fitting 30 is communicated withsuction chamber 48 fluids with suction circuit 254.Outlet fitting 38 is communicated withdrain line 256 fluids, the working fluid through overcompression that drainline 256 receives from thedrain chamber 46 of compressor 20.Inlet fitting 42 forms intermediate pressure port, and intermediate pressure port is communicated with at the compression chamber corresponding to thescroll component 64 in the position of the intermediate pressure between discharge pressure and the suction pressure and the compressor 20.Therefore, inlet fitting 42 can be given the compression chamber accommodating fluid ofcompressor 20 at the intermediate pressure position place.

The discharging working fluid that flows throughdrain line 256 flows in thecondenser 258, wherein, and heat Q₁From the working fluid that flows through, discharge.Heat Q₁Can be released to another fluid that flows through condenser 258.As nonrestrictive example, heat Q₁Can be delivered to theair stream 261 that imports and flow throughcondenser 258 by fan 260.The working fluid that flows throughcondenser 258 can be condensed into the high pressure liquid condensed working fluid that temperature reduces from the vapor phase working fluid of high temperature, high pressure.

The working fluid of condensation via condensation workingfluid circuit 262 fromcondenser 258 inflow heat exchangers 32.The working fluid of condensation can get into the top ofheat exchanger 32 through accessory 264.Working fluid leavesheat exchanger 32 through another circuit 266.Circuit 266 can be coupled to the bottom ofheat exchanger 32 and be communicated with it via accessory 268.Be described below, inheat exchanger 32, heat Q₂From the condensation working fluid that flows through, discharge.As a result, the working fluid secondary of condensation cooling and leaveheat exchanger 32 with the temperature that is lower than when getting intoheat exchanger 32.

Secondary cooling condensation working fluid in thecircuit 266 flows through main the saving or expansion gear 270.The working fluid that flows throughexpansion gear 270 expands, and is accompanied by reducing of pressure and the further reduction of appearance temperature.Can dynamically controlexpansion gear 270 and be placed on the varying duty on therefrigeration system 250 with compensation.Alternately,expansion gear 270 can be static.

The expanded working fluid current throughline 272 inexpansion gear 270 downstream gets intovaporizer 274.In vaporizer 274, working fluid absorbs heat Q₃And can change the low pressure steam attitude working fluid that temperature raises into from the liquid working fluid of low temperature, low pressure.As nonrestrictive example, by the heat Q of working fluid absorption₃Can extract from importing throughfan 278 and flowing through theair stream 276 ofvaporizer 274.

Suck circuit 254 and be coupled tovaporizer 274, the feasible working fluid that leavesvaporizer 274 flows throughsuction circuit 254 and turns back in thesuction chamber 48 ofcompressor 20, thereby forms locking system.

As top described, can also flow throughheat exchanger 32 from the oiling agent ofcompressor 20 about compressor 20.Especially, through the pressure difference betweendrain chamber 46 and thesuction chamber 48, oiling agent can flow throughheat exchanger 32 and turns back to thesuction chamber 48 from drain chamber46.In heat exchanger 32, heat Q₄Can from the oiling agent that flows through, discharge.As a result, the temperature of leaving the oiling agent ofheat exchanger 32 is lower than the temperature of the oiling agent that gets intoheat exchanger 32.

Compressor 20 utilizes the condensation working fluid that expands inheat exchanger 32, to absorb heat Q withrefrigeration system 250₂With heat Q₄Especially, practice thrift the loop and can be used for the condensation working fluid in the second cooling heat exchanger 32.Secondary cooling condensation working fluid can improve working fluid and invaporizer 274, absorbs heat Q before working fluid flows throughexpansion gear 270₃Capacity and therefore improve the cooling capacity ofrefrigeration system 250.

For secondary cooling is provided, the part of working fluid that flows through thecircuit 266 inheat exchanger 32 downstream can through and savingroute 280, in practicingthrift expansion gear 282, expand (thereby reducing temperature and pressure), and pass through incircuit 284 delivery heat exchangers 32.Especially, practice thrift the bottom that working fluid can arriveheat exchanger 32 through accessory 286.The liquid-vapor attitude that working fluid can be liquid state, steam state or two phases is practiced thrift in expansion in the circuit 284.Practicing thrift working fluid can upwards flow throughheat exchanger 32 and get into theinfusion line 288 that links to each other with the inlet fitting 42 of dividing plate 26.Especially, practice thrift the top that working fluid can leaveheat exchanger 32 through theaccessory 290 that is coupled toinfusion line 288.

Inheat exchanger 32, practice thrift working fluid and from the condensation working fluid that gets intoheat exchanger 32 throughcircuit 262, absorb heat Q₂, make the temperature of working fluid of condensation reduce (just, by the secondary cooling).The saving working fluid that leavesheat exchanger 32 throughinfusion line 288 is through inlet fitting 42 andradial passage 166,branch 168,branch 170 and decide the intermediate pressure position that opening 170 in thevortex 62 is expelled to scrollcomponent 64.

Compressor 20 advantageously uses withrefrigeration system 250 and practices thrift the oiling agent that coolstream overcompression machine 20 is come in the loop.Especially, inheat exchanger 32, heat Q₄Be delivered to the saving working fluid from oiling agent.As a result, the temperature via the oiling agent ofcircuit 214outflow heat exchangers 32 reduces.Thereforeheat exchanger 32 plays the effect of double system heat exchanger.

Expansion gear 282 can be dynamic apparatus or staticizer as required, with the reduction effect that expectation is provided and the cooling of oilingagent.Expansion gear 282 can keep injecting the pressure that route 288 interior pressure are higher than the intermediate pressure position place of the compression chamber that is communicated with inlet fitting 42.The working fluid that is expelled to intermediate pressure position can be the liquid-vapor attitude of steam state, liquid state or two phases.The saving working fluid is expelled to the intermediate pressure position ofscroll component 64 and can advantageously cools off vortex and reduce exhaust temperature.

Useheat exchanger 32 to extract heat Q₂With heat Q₄Lower complexity and/or more cheap refrigeration system can be provided, and wherein, single heat exchanger can provide the secondary cooling of condensation working fluid and the cooling of oiling agent.In addition, use practicing thrift working fluid comes coolant/lubricant to eliminate the demand of that separate or the different cooling systems that is used for oiling agent and possibly use the for example cold water demand of coming coolant/lubricant of different media.And, these feature sets are formed insingle heat exchanger 32 allow heat exchanger to be readily integrated in thecompressor 20, thereby can realize compacter design and reduce the zone that system occupies.

Alternatively, practice thrift the condensed refrigerant that the loop can utilizecondenser 258 downstream andheat exchanger 32 upper reaches.Especially, shown in the dotted line among Figure 14, practice thrift circuit 280 ' and can extend toexpansion gear 282 from circuit 262.In this case, do not use saving circuit 280.As a result, thus a part that flows through the condensation working fluid ofcircuit 262 forms the saving working fluid stream that flows throughheat exchanger 32 through practicing thrift circuit 280 ' and arrivingexpansion gear 282 and expand.The remaining operation ofrefrigeration system 250 is identical with top discussion.

With reference now to Figure 15,, in refrigeration system 300, schematically shows a kind of alternate configuration that is used for coolant/lubricant.Refrigeration system 300 is similar with therefrigeration system 250 of top discussion, and uses identical reference number to indicate identical or similar parts, circuit, characteristic etc.Like this, only the main difference part between refrigeration system 300 and therefrigeration system 250 is at length discussed.

A difference of refrigeration system 300 is not use single double system heat exchanger 32.On the contrary, two heat exchangers that separate 302,304 in refrigeration system 300, have been used.In refrigeration system 300, heat exchanger 302 comes the secondary cool stream to cross the working fluid of condensation wherein as economizer heat exchanger, and heat exchanger 304 plays the action of temperature that reduces the oiling agent wherein of flowing through.Especially, circuit 305 extends to heat exchanger 302 and guides expanded working fluid to get into heat exchanger 302 from expansion gear 282.In heat exchanger 302, heat Q₂Absorbed from the expansion working fluid that gets into the condensation working fluid of heat exchanger 302 through circuit 262.As a result, the working fluid secondary cooling that in heat exchanger 302, is inflated of the working fluid of condensation.

Expanded working fluid is left heat exchanger 302 and inflow heat exchanger 304 through circuit 306.Heat exchanger 304 is as the oiling agent heat exchanger.Oiling agent circuit 210 extends to the heat exchanger 304 fromcompressor 20, and oilingagent return line 214 is got back tocompressor 20 from heat exchanger 304 extensions.In heat exchanger 304, heat Q₄From the oiling agent of flowing through wherein, discharge and be delivered on the expansion working fluid that flows through heat exchanger 304.As a result, the temperature that flows through the oiling agent of heat exchanger 304 reduces.

Expanded working fluid is left heat exchanger 304, and as stated, is injected into the intermediate pressure position in thescroll component 64 in thecompressor 20 through infusion line 288.The expanded working fluid that flows through heat exchanger 302,304 can get into the liquid-vapor attitude of liquid state, steam state or two phases wherein and therefrom to be left.

Alternatively, in refrigeration system 300, can cancel the secondary cooling of condensation working fluid.In this layout, heat exchanger 302 andcircuit 266 and circuit 306 will not appear.On the contrary, the working fluid of condensation extracted fromcircuit 262 before flowing throughexpansion gear 270, expanded throughexpansion gear 282, and offered heat exchanger 304 through expansion working fluid circuit 305 ' (showing with dotted line).In this structure, be used to from the oiling agent that flows through heat exchanger 304, absorb single heat Q byexpansion gear 282 expanded working fluid₄As a result, come the temperature of the oiling agent of automatic heat-exchanger 304 to reduce.As stated, the expansion working fluid that leaves heat exchanger 304 is expelled to the intermediate pressure position ofcompressor 20 throughinfusion line 288.

Therefore, in refrigeration system 300, the working fluid of condensation can be inflated and be used for the working fluid of secondary cooling condensation and/or the oiling agent of cool stream overcompression machine 20.Use the expansion working fluid to help reducing system complex degree and cost through eliminating demand to the different external refrigeration media that is used for coolant/lubricant.In addition, the use of expansion working fluid can realize saving the structure in space, and wherein, heat exchanger 302 and/or heat exchanger 304 can attach to compressor 20.As a result, can realize having the saving in space system of the system's floor space that reduces.

Therefore, thus can advantageously be utilized in the working fluid of the condensation that expands the temperature that reduces the oiling agent that flows through compressor subsequently according to the compressor of the utility model and refrigeration system.The saving loop that the cooling of oiling agent can utilize the working fluid to condensation to carry out the secondary cooling is regulated.As a result, do not need outside cooling medium or cooling source to come coolant/lubricant.In addition, to compressor, can realize compacter design through attached one or more heat exchangers.In some embodiments, the double system heat exchanger can be used to the working fluid and the coolant/lubricant of secondary cooling condensation.In other mode of executions, utilized independent heat exchanger.In some embodiments, can under the situation that does not have the liquid working fluid circuit of secondary cooling condensation, use expanded working fluid, wherein, have only oiling agent to pass through the expanded working fluid cooling.In all these mode of executions, the expansion working fluid of heat absorption is expelled to the intermediate pressure position of compressor.The reduction of lubricant temperature can cause lower injection lubricant temperature, and this can reduce the suction gas superheat, thereby improves compressor volume efficient and improve performance.In addition, the lubricant temperature of reduction can improve the reliability of compressor owing to suck the cooling of gas and motor, and can keep desirable levels of viscosity and realize thickness suitable between the compressor moving element.

Various finished surfaces be combined in advantageously helped in the compressor case accurate centering of various parts in compressor with axially on accurate aligning.The processing of shell can be provided with completion through single, makes thereby provide efficiently.In addition, finished surface all is a circular feature, thereby has promoted simple processing.The parts that engage with the shell finished surface also can be made efficiently.Therefore, compressor can provide better aligning and/or make efficiently.

In compressor, form middle groove between main bearing seat and the thrust plate and advantageously promoted lubricating of moving vortex and associated components.Thrust plate, shell and main bearing seat can limit middle groove.Help it and pass the oiling agent in the middle groove and oiling agent is splashed on the parts in middle groove zone on bent axle, comprising counterweight between main bearing seat and the moving vortex.Can in shell, process the bypass groove, thereby allow oiling agent to flow to down the vortex import from motor zone (downside) so that walk around middle groove.

Although the utility model illustrates on horizontal-type compressor, wherein motor is positioned at shell, and the utility model also can use in the opening driven compressor, and wherein, motor is positioned at the outside of shell and drives the axle that passes shell.

After the utility model has been carried out above description, it is apparent that the utility model possibly change in many ways.These change does not think aim and the scope that departs from the utility model, and is intended to make all these changes that it will be apparent to those skilled in the art that all to be included in the scope of claim.

Claims (12)

1. compressor is characterized in that comprising:

The integral type main body; Said main body comprises the shell integrally formed with main bearing seat; Said main bearing seat has the hole of a part that is used to support bent axle; Said shell comprises the continuous circular shape surface of the first end of contiguous said shell on the inside of said shell and a plurality of axially extended arcuate surface of the second end of contiguous said shell, and said a plurality of arcuate surface are opened along the said internal layout of said shell.

2. compressor as claimed in claim 1; Wherein, Said compressor further comprises the scroll element with outer surface; The size of said outer surface is set to be coupled in the said first end of said shell and with said annular surface and engages, and said annular surface makes said scroll element centering in said shell.

3. compressor as claimed in claim 1; Wherein, Said compressor further comprises the dividing plate with edge; The size at the edge of said dividing plate is set to be coupled in the said first end of said shell and with said annular surface and engages, and said annular surface makes said dividing plate with respect to said shell centering.

4. compressor as claimed in claim 1; Wherein, said compressor further comprises the stator with outer surface, and the size of said outer surface is set to be contained in the said shell; Said outer surface engages with said arcuate surface, and said arcuate surface makes said stator centering in said shell.

5. compressor as claimed in claim 2, wherein, said compressor further comprises:

Shoulder in the said shell between said main bearing seat and said annular surface; With

Thrust plate, said thrust plate have first surface that engages with said scroll element and the second surface that engages with said shoulder, and said shoulder limits the axial position of said thrust plate in said shell.

6. compressor as claimed in claim 5, wherein, said main bearing seat and said thrust plate limit the downside lubricant tank jointly.

7. compressor as claimed in claim 6; Wherein, Said compressor further comprises bent axle and counterweight, and said bent axle engages with said scroll element driven nature, and said counterweight attaches to said bent axle and rotates along with the rotation of said bent axle; Said counterweight is passed the oiling agent in the said downside lubricant tank and wherein the said oiling agent of splashing during said crankshaft rotating, thus with said lubricant delivery to said scroll element.

8. compressor as claimed in claim 6; Wherein, Said compressor further comprises the end cap with edge; The size at the edge of said end cap is set to be coupled in the said the second end of said shell and with said arcuate surface and engages, and said end cap has the hole of the end that is used to support said bent axle, and said arcuate surface makes said end cap with respect to said shell centering and said hole and the said hole in the said main bearing seat in the said end cap are axially aligned.

9. compressor as claimed in claim 8, wherein, said end cap is limited with high side lubricant tank.

10. compressor as claimed in claim 9, wherein, said end cap comprises the oiling agent outlet fitting that is communicated with said high side lubricant tank and heat exchanger fluid.

11. compressor as claimed in claim 10; Wherein, Said heat exchanger comprises the first fluid passage and second fluid passage that receive from the working fluid of said compressor of reception from the oiling agent of said high side lubricant tank, and the said first fluid passage and second fluid passage be fluid isolation each other.

12. compressor as claimed in claim 11, wherein, said scroll element is limited with the intermediate pressure position of reception from the expanded working fluid of said heat exchanger.

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